Breakaway assembly

ABSTRACT

A breakaway assembly including a first connector and a second connector releasably coupleable to the first connector. The assembly is movable between a first configuration in which the first and second connectors are releasably coupled and together define a fluid path through which fluid is flowable, wherein the fluid path includes an at least partially radially extending portion, and a second configuration in which the first and second connectors are not coupled together. The assembly is configured to move from the first configuration to the second configuration when a predetermined separation force is applied to the assembly. The assembly further includes a closure valve positioned in one of the first or second connectors, wherein the closure valve is configured to be in an open position when the assembly is in the first configuration to allow fluid to flow therethrough, and to move to a closed position blocking the at least partially radially extending portion of the fluid path when the assembly moves to the second configuration to generally block the flow of fluid therethrough.

BACKGROUND

Breakaway connectors or assemblies can be utilized in fluid dispensingsystems, such as refueling stations and the like. The breakawayassemblies are designed to provide a break in the fluid system which canbe closed when a sufficient, predefined separation force is appliedthereto. For example, in a drive-away event, the user of a refuelingunit may inadvertently leave the nozzle in the tank of a vehicle orautomobile and drive away. Breakaway assemblies are designed to providea breakaway point at which the hose or system can be separated, and alsoprovide a closing valve to prevent or minimize loss of fuel. However,many current breakaway assemblies have various drawbacks.

Single use breakaways typically use shear pins or shear grooves, butsuch shear elements cannot be fully tested during assembly, which canlead to unpredictable performance. Many existing reconnectablebreakaways use using garter springs, canted coil springs, compressionsprings and deflectable members to provide a releasable connectionmechanism. However such releasable connection mechanisms can haverelatively high variances in the materials and/or tolerances, and thuslead to unpredictable separation force.

Existing breakaways can also have issues accommodating pressure pulsesin the dispensed fluid. Since single use breakaways use a rigid memberthat is designed to shear or break when sufficient force is applied, andsuch components can undesirably separate when a sufficiently powerfulpressure pulse is transmitted. Reconnectable breakaways can also beprone to separation due to force or pressure spikes and/or internalcomponents can be damaged due to the force or pressure spike.

Finally, existing breakaways typically have valves that are designed toclose after a breakaway event. However the valves may not close in asufficiently predictable manner.

SUMMARY

In one embodiment, the present invention is a breakaway assembly that isreconnectable, provides a relatively consistent separation force, in onecases using magnets, in one case which can accommodate force or pressurespikes, and in one case provides an improved closure valve arrangement.More particularly, in one embodiment, the invention is a breakawayassembly including a first connector and a second connector releasablycoupleable to the first connector. The assembly is movable between afirst configuration in which the first and second connectors arereleasably coupled and together define a fluid path through which fluidis flowable, wherein the fluid path includes an at least partiallyradially extending portion, and a second configuration in which thefirst and second connectors are not coupled together. The assembly isconfigured to move from the first configuration to the secondconfiguration when a predetermined separation force is applied to theassembly. The assembly further includes a closure valve positioned inone of the first or second connectors, wherein the closure valve isconfigured to be in an open position when the assembly is in the firstconfiguration to allow fluid to flow therethrough, and to move to aclosed position blocking the at least partially radially extendingportion of the fluid path when the assembly moves to the secondconfiguration to generally block the flow of fluid therethrough.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic representation of a refueling system utilizing abreakaway assembly;

FIG. 1A is a detail view of the area indicated in FIG. 1 ;

FIG. 2 is a side cross sectional view of one embodiment of a breakawayassembly, shown in its connected configuration;

FIG. 3 is a side cross sectional view of the breakaway assembly of FIG.2 , shown in its disconnected configuration;

FIG. 4 is front perspective view of the magnet unit of the breakawayassembly of FIG. 2 , shown partially disassembled;

FIG. 5 is a front perspective view of the magnet unit of FIG. 4 , shownin an assembled condition;

FIG. 6 is a cross section taken along line 6-6 of FIG. 5 ;

FIG. 7 is a cross section of an alternate configuration of the magnetunit of FIG. 4 ;

FIG. 8 is a cross section of an alternate configuration of the magnetunit of FIG. 4 ;

FIG. 9 is a cross section of an alternate configuration of the magnetunit of FIG. 4 ;

FIG. 10 is a cross section of an alternate configuration of the magnetunit of FIG. 4 ;

FIG. 11 is a cross section of an alternate configuration of the magnetunit of FIG. 4 ;

FIG. 12 is a front perspective view of an alternate embodiment of themagnet unit of FIGS. 4 and 5 ;

FIG. 13 is a side cross sectional view of the breakaway assembly of FIG.2 , shown accommodating a force spike;

FIG. 13A is a detail view of the area indicated in FIG. 13 ;

FIG. 14 is a side cross sectional view of another breakaway assembly;

FIG. 15 is an cross-sectional view of the magnet unit of the breakawayassembly of FIG. 14 , taken along line 15-15;

FIG. 15A is a side perspective view of a magnet retainer of the magnetunit of FIG. 15 ;

FIG. 16 is a detail cross section of the area indicated in FIG. 13Ashowing another embodiment of the breakaway assembly with a magneticassembly for accommodating a force spike;

FIG. 16A shows the components of FIG. 16 in the process of accommodatinga force spike;

FIG. 17 is a side cross sectional view of another embodiment of abreakaway assembly, shown in its connected configuration;

FIG. 18 is a side cross sectional view of the breakaway assembly of FIG.17 , with the shuttle moved downstream as a step of disconnection;

FIG. 19 is a side cross sectional view of the breakaway assembly of FIG.17 , shown in its disconnected configuration;

FIG. 20 is a detail cross section of the area indicated in FIG. 17 ,shown accommodating a force spike;

FIG. 21 is a side cross sectional view of the breakaway assembly of FIG.17 , shown in conjunction with a reconnection tool; and

FIG. 22 is a side cross sectional view of the breakaway assembly of FIG.21 , shown in its connected configuration.

DETAILED DESCRIPTION

System Overview

FIG. 1 is a schematic representation of a refilling system 10 includinga plurality of dispensers 12. Each dispenser 12 includes a dispenserbody 14, a hose 16 coupled to the dispenser body 14, and a nozzle 18positioned at the distal end of the hose 16. Each hose 16 may begenerally flexible and pliable to allow the hose 16 and nozzle 18 to bepositioned in a convenient refilling position as desired by theuser/operator.

Each dispenser 12 is in fluid communication with a fuel/fluid storagetank 20 via a liquid or fluid conduit or path 22 that extends from eachdispenser 12 to the storage tank 20. The storage tank 20 includes or isfluidly coupled to a fuel pump 24 which is configured to draw fluid/fuelout of the storage tank 20 via a pipe 26. During refilling, as shown bythe in-use dispenser 12′ of FIG. 1 , the nozzle 18 is inserted into afill pipe 28 of a vehicle fuel tank 30. The fuel pump 24 is thenactivated to pump fuel from the storage tank 20 to the fluid conduit 22,hose 16 and nozzle 18 and into the vehicle fuel tank 30 via a fuel orfluid path or fluid conduit 32 of the system 10.

In some cases, the system 10 may also include a vapor path 34 extendingfrom the nozzle 18, through the hose 16 and a vapor conduit 36 to theullage space of the tank 20. For example, as shown in FIG. 1A, in oneembodiment the vapor path 34 of the hose 16 is received in, andgenerally coaxial with, an outer fluid path 32 of the hose 16. Thenozzle 18 may include a flexible vapor boot or bellows, sleeve or thelike (not shown) of the type well known in the art which is coupled to,and circumferentially extends around, a spout 40 of the nozzle 18.

The bellows is designed to form a seal about the spout 40 when the spout40 is inserted into the fill pipe 28. The bellows help to capture vaporsand route the vapors into the vapor path 34, although vapors can also becaptured with nozzles 18 lacking a bellows. The system 10 may include avapor recovery pump 25 which applies a suction force to the vapor path34 to aid in vapor recovery, although in some cases (e.g. so-called“balance” systems) the vapor recovery pump 25 may be omitted. Inaddition, in some cases the system 10 may lack the vapor path 34, inwhich case the system 10 may lack the vapor conduit 36, and the hose 16may lack the vapor path 34 therein.

The system 10 disclosed herein can be utilized to store/dispense any ofa wide variety of fluids, liquids or fuels, including but not limited topetroleum-based fuels, such as gasoline, diesel, natural gas (includingcompressed natural gas (CNG)), biofuels, blended fuels, propane orliquefied petroleum gas (LPG), oil or the like, or other fuels orliquids such as hydrogen, ethanol the like,

Each dispenser 12 may include a breakaway assembly 42 associatedtherewith, which can be located at various positions on the dispenser12, or along the system 10. For example, the left-most dispenser 12′ ofFIG. 1 utilizes a breakaway assembly 42 at the base end of the hose 16;the middle dispenser 12 of FIG. 1 utilizes a breakaway assembly 42positioned adjacent to the nozzle 18; and the right-most dispenser 12 ofFIG. 1 utilizes a breakaway assembly or assembly 42 at an intermediateposition of the hose 16. However, it should be understood that thebreakaway assembly 42 can be positioned at any of a wide variety ofpositions along the length of the hose 16, or at other positions in therefueling system 10. The breakaway assembly 42 may include, and/or becoupled to, a swivel assembly to enable the breakaway assembly 42 toassume various positions and become aligned with any separation forcesapplied thereto.

Breakaway Overview

FIGS. 2 and 3 illustrate one embodiment of the breakaway assembly 42,for use with conventional (typically liquid) fuels such as gasoline,diesel, oil or the like that are pumped under relatively low pressure,such as less than about 50 psi in one case, or less than about 100 psiin another case, or less than about 150 psi in another case, or lessthan about 300 psi in yet another case. The breakaway assembly 42includes a first or upstream connector 44 releasably connected to asecond or downstream connector 46. The breakaway assembly 42 andconnectors 44, 46, are generally annular in one case, with the fluidpath 32 positioned therein, but can have other shapes as desired. Thefirst connector 44 may be connected to an upstream portion of the system10/hose 16, and the second connector 46 may be connected to a downstreamportion of the system 10/hose 16 (it should be understood that termsused in relation to the direction of flow, such as “upstream” and“downstream,” are used herein with respect to the direction of the flowof fluids/fuel to be dispersed (i.e. right-to-left in FIGS. 2, 3, 13 and14 , and left-to-right in FIGS. 17-19 , as opposed to for example thedirection of vapor flow, unless specified otherwise). However, ifdesired this orientation may be reversed such that first connector 44 isconnected to a downstream component, and the second connector 46 isconnected to an upstream component. Both the first connector 44 andsecond connector 46 can include threaded surfaces (such as theillustrated internal threaded surfaces or threaded adapters 48) forsecuring the connectors 44, 46 to the associated upstream and downstreamcomponents. The threaded surfaces 48 could instead take the form ofexternally threaded surfaces, or various other coupling structuresbesides threaded surfaces may be used.

The first connector 44 may include a generally tubular or annularcoupling portion 50, which can have a variety of shapes in crosssection, and which can be removably receivable in a socket or protectivecover 52 of the second connector 46. The second connector 46 furtherincludes a closure valve or poppet valve 54 positioned therein. Thepoppet valve 54 includes a body portion 56 having a downstream stem 58,an upstream stem 62, and seal or sealing portion 64 coupled to the bodyportion 56. The downstream stem 58 is slidably received in a guide 66which is positioned or centered in the second connector 46 by aplurality of radially-extending fins 68. The poppet valve 54 furtherincludes a spring 74 positioned axially between the guide 66 and thebody portion 56. The body portion 56/poppet valve 54 is thereby biased,by the spring 74, to an upstream/closed position in which the sealingportion 64 sealingly engages the poppet valve seat 76 (see FIG. 3 ). Thesecond connector 46 may include a seal 47 on a radially outer surface ofits axially-forwardly extending end to help form a seal with the innersurface of the first connector 44.

The first connector 44 may include a closure valve or poppet valve 80positioned therein. The poppet valve 80 includes a body portion 82having a downstream stem 84, an upstream stem 86, and seal or sealingportion 88 coupled to the body portion 82. The upstream stem 86 isslidably received in a guide 90 which is positioned/centered in thefirst connector 44 by a plurality of radially-extending fins 92. Thepoppet valve 80 further includes a spring 94 positioned between theguide 90 and the body portion 82. The body portion 82/poppet valve 80 isthereby biased, by the spring 94, to a downstream/closed position inwhich the sealing portion 88 sealingly engages the poppet valve seat 96(see FIG. 3 ).

During normal operation of a dispenser 12, the first connector 44 andsecond connector 46 are arranged in their first/locked/connected/engagedstate or configuration, as shown in FIG. 2 , in which the first 44 andsecond 46 connectors are coupled together and define an open fluidconduit, or fluid path 32 through which fluid may flow, as shown by thearrows of FIG. 2 . In this configuration, the upstream stem 62 of thepoppet valve 54 engages and moves the downstream stem 84 of poppet valve80 away from its valve seat 96, and vice versa, such that the springs74, 94 of both poppet valves 54, 80 are compressed and both poppetvalves 54, 80 are opened. When the poppet valves 54, 80 are opened theseals 64, 88 are spaced away from their associated seats 76, 96,enabling fluid to flow through the fluid path 32/breakaway assembly42/connectors 44, 46. As will be described in greater detail below, acoupling mechanism or coupling system 41 is provided to releasablycouple the connectors 44, 46 in the axial direction.

When sufficient separation forces are applied to the assembly 42 (i.e.forces applied at least partially along the axis of the breakawayassembly 42/connectors 44, 46), the coupling mechanism 41releases/separates and the breakaway assembly 42 moves to itssecond/separated/disconnected state or configuration as shown in FIG. 3. When the connectors 44, 46 are moved away from each other, thedownstream stem 84 of the poppet valve 80 is pulled away from theupstream stem 62 of poppet valve 54. The relative movement of theconnector(s) 44, 46 away from each other enables the poppet valves 54,80 to move to their closed positions, as shown in FIG. 3 in which theseals 64, 88 engage their associated valve seats 76, 96, as biased bytheir associated springs 74, 94.

The assembly 42 may be reusable and may be configured such that theconnectors 44, 46 are connectable/reconnectable (i.e. movable from theconfiguration of FIG. 3 to that of FIG. 2 ) without requiring any repairor replacement of any components of the assembly 42. In particular, whenthe first connector 44 and second connector 46 areconnected/reconnected, the downstream stem 84 of the poppet valve 80engages the upstream stem 62 of the poppet valve 54. When sufficientaxial compression forces are applied to the assembly 42 during thereconnection process, the body portions 56, 82 of the poppet valves 54,80 and associated seals 64, 88 are moved away from their respectivevalve seats 76, 96 until the valves 54, 80 are in the position shown inFIG. 2 .

The illustrated embodiment shows both the first 44 and second 46connectors having poppet valves 54, 80 therein. However, in an alternateembodiment, only one of the connectors 44, 46 has a poppet valve. Inthis case, the other connector 44, 46, lacking a poppet valve, mayinclude a rigid, axially-extending hold-open stand, analogous to theportions 62/84, which extends axially forwardly and can engage thepoppet valve (e.g. valve 54, 80) in the other connector 44, 46 and urgethe other poppet valve to the open position when the assembly 42 is inits connected configuration. In yet another alternate embodiment, whenthe assembly 42 is used with dispensing systems utilizing vapor recoverysystems, one or both of the connectors 44, 46 may include poppet valvesin or at least partially defining the vapor path 34 which are openedwhen the assembly 42 is in the connected configuration, and whichautomatically close when the assembly 42 moves to the disconnectedposition. Examples of these arrangements are disclosed in U.S. Pat. No.8,931,499, the entire contents of which are hereby incorporated byreference herein.

Magnetic Coupling/Breakaway

The assembly 42 may include the coupling mechanism 41 which releasablycouples the connectors 44, 46 together to retain the assembly 42 in itscoupled position until sufficient axial forces are applied. The couplingmechanism 41 may include a magnet unit 43, which includes a magnetcoupler 102 that receives various magnets 104 therein. The magnet unit43 is coupled to the first connector 44 in the illustrated embodiment.The coupling mechanism 41 can also include an attraction member 106 (orother member which completes the magnetic circuit) which can be made ofa ferrous material or other material that is magnetically attracted orattractable to the magnets 104/magnet unit 43. The attraction member 106is coupled to the second connector 46 in the illustrated embodiment. Inthe particular illustrated embodiment the magnet unit 43 constitutes ordefines the coupling portion 50 of the first connector 44 that isreceived in the socket/cover 52 of the second connector 46. If desired,the positioning of the magnet unit 43 and attraction member 106 can bereversed from that shown such that the attraction member 106 is coupledto the first connector 44, and the magnet unit 43 is coupled to thesecond connector 46.

In one embodiment the attraction member 106 is generally annular andmade of a ferrous material or other magnetizable material, and directlythreadably attached to the body of the first connector 44. Theattraction member 106 could instead be made of or include a magnet ormagnets configured and arranged to be magnetically attracted to anassociated magnet(s) 104 of the magnet unit 43 when properly aligned.Further alternately, rather than being a continuous annular member, theattraction member 106 can instead take the form of various, discrete andspaced apart attraction member units or portions positioned tomagnetically interact with the magnet unit 43.

The magnets 104 of the magnet unit 43 can be made of any of a widevariety of materials, including permanently magnetized materials such asrare earth magnets, including neodymium in one case. The magnet coupler102 and/or attraction member 106 can be made of a magnetized and/ormagnetizable material such as ferromagnetic material or metal (iron,cobalt, nickel, manganese, gadolinium, dysprosium or others),paramagnetic materials, diamagnetic materials, ferrimagnet metals,ferromagnetic alloys, sheet steel or cast steel, or in some casesnon-magnetized or non-magnetizable material, each of which can ifdesired be covered with a ferromagnetic coating or plating, such asnickel in one case but could be nearly any ferromagnetic metal or alloywhich will not unduly interfere with any potentially desired magneticfield. The magnets 104 and/or magnet coupler 102 and/or attractionmember 106 can be plated, coated, encapsulated or unplated.

In one case the magnet coupler 102 and/or attraction member 106 canhave, or be made of a material having, a saturation point that isgreater than about 1.25 Tesla to provide the desired ferromagneticresponse. In particular, it may be desired to have the magnet coupler102, as energized/magnetized by the magnets 104 received therein,magnetically interact with the attraction member 106 as a unit, ratherthan have the individual magnets 104 directly magnetically interact withthe attraction member 106. The magnet coupler 102 can thus beconfigured, sized and shaped to direct the magnet field in a desired andadvantageous manner. In particular, by passing the induced magneticfield through the magnet coupler 102, the magnetic field linesoriginating with the magnets 104 tend to pass through the radially inner108 and radially outer 110 annular components or surfaces of the magnetcoupler 102 (and not, for example, through the web or end wall 112 atthe base of the magnet coupler 102), which provides a stronger magneticforce since the web 112 acts as a shunting member. Moreover, since theweb 112 acts as a shunting member it may be desired to avoid or minimizethe magnetic field lines passing through the web 112, and thus may bedesired to keep the web 112 as thin as possible.

The web 112 may have a thickness (e.g. in the axial direction) thatallows the greatest amount of magnetic flux field to pass into/throughthe magnet coupler 102, which is dependent on a balance of factors,including the strength of the magnetic field, and the permeability andsaturation limits of the materials of the magnet coupler 102. The ratioof the thickness of the web 112, to the field penetration depth, maybetween about 5% and about 15% in one case, where the field penetrationdepth is dependent on the saturation point of the material of the magnetcoupler 102. In a case where the magnetic flux density is between 1.25 Tand 2 T, the field penetration depth can be between 0.25″ and 0.625″,and the thickness of the web 112 can range from 0.0125″ to 0.09375″. Inone case the web 112 has an axial length of less than about 25% in onecase, or less than 10% in another case, or less than 5% in another case,or less than 2.5% in another case of a length of the magnets 104 and/orlength of the magnet unit 43. In some cases it may be desired toeliminate the web 112 entirely for magnetic performance, but doing socould create difficulties in physically retaining the magnets 104 in thedesired axial position in the magnet coupler 102. In some cases the web112 can be slotted or have other openings to reduce the shunting effectof the web 112.

The attraction member 106 and magnet unit 43 can thus form the couplingmechanism 41 that releasably couples the connectors 44, 46 together andtends to retain the assembly 42 in its first/locked/connected/engagedstate or configuration, as shown in FIG. 2 . The coupling mechanism 41may thus solely or primarily determine the separation force of thebreakaway assembly 42.

When an external axial force is applied to the breakaway assembly 42that is greater than the attractive force of the magnet unit 43 to theattraction member 106, a separation will occur in the followingsequence. The downstream connector 46 will first move away from theupstream connector 44, along with nearly all associated portions of thedownstream connector 46 (e.g. except for the associated poppet valve 54which may begin to close). Both poppet valves 54, 80 may simultaneouslystart move to their closed position. In one case, after roughly ¼″ oftravel of the connectors 44, 46 away from each other, both poppet valves54, 80 will be fully moved to their closed positioned. As the separationmotion continues, at a greater distance, about 5/16″ of travel in onecase, the upstream connector 44 will be fully extracted out of thesocket 52 of the downstream connector 46 (shown as nearly fullyextracted in FIG. 3 ). In this state the connectors 44, 46 are separatedand the poppet valves 80, 54 are closed to prevent or limit the leakageof fluid.

After the connectors 44, 46 are separated, it may then desired toreconnect the connectors 44, 46. In one case the connectors 44, 46, canbe axially aligned and manually pressed together such that the magnetunit 43 fits into the socket 52. The connectors 44, 46 are then pressedtogether, and the springs 94, 74 compressed until the poppet valves 80,54 are open as shown in FIG. 2 . During a reconnection event, since theattraction member 106 is positioned on or in the downstream connector46, the magnet unit 43 will be at some point during insertion besufficiently attracted to the attraction member 106 such that the magnetunit 43/assembly 42 may be felt to “snap” into place. In addition, theattraction between the magnet unit 43 and the attraction member 106 mayreduce the reconnection force and act as a magnetic assist feature,aiding a user in reconnection. Thus the (manual) force required toconnect the first 44 and second 46 connectors can be less than the forcerequired to separate the first 44 and second 46 connectors in abreakaway event, which can provide an easier and more convenientreconnection process.

Magnet Coupler Configuration

In the embodiment shown in FIGS. 2-6 , the magnet coupler 102 has anupstream portion 102 a with an annular channel or channel portion 114formed therein, that is removably attachable to a downstream portion 102b with a correspondingly shaped and located channel or channel portion116. Each portion 102 a, 102 b can have a web or end wall 112 positionedat an axial end of the portion 102 a, 102 b and positioned adjacent tothe associated channel 114, 116. The upstream 102 a and downstream 102 bportions can be separate components or parts that are coupled togetherat or along a joint 105 that is aligned in a radial plane. One or bothchannel portions 114, 116 can receive the magnets 104 therein. Eachmagnet coupler portions 102 a, 102 b can include a threaded surface 103thereon, where the threaded surfaces 103 are configured to threadablyengage each other to form the generally closed magnet coupler 102 shownin FIG. 4 (when assembled) and FIG. 5 . When the magnet unit 43 is fullyassembled by joining the upstream 102 a and downstream 102 b portions bymechanical, releasable or other means an internal, closed channel 114,116 is formed therein that receives and encapsulates the magnets 104therein.

In the illustrated embodiment and with reference to FIG. 4 , in one caseeach magnet 104 is shaped as a rectangular prism and the poles 118, 120of the magnets 104 are oriented perpendicular to the largest face of themagnet 104. In one case the magnets 104 are arranged with their northpoles 118 positioned on (extending perpendicular to) the radially innerfaces of the magnets 104, and their south poles 120 positioned on(extending perpendicular to) the radially outer faces of the magnets104. Thus the poles 118, 120 of the magnets 104 can be orientedperpendicular to the central axis A (FIG. 2 ) of the assembly 42, ornon-parallel with axis A, and aligned with a radial line pointingradially inwardly or outwardly.

As shown in FIG. 6 , in one case the channel 114 of the upstream portion102 a can be formed in end view as a prism with a number of sides(twelve sides in the illustrated embodiment) that corresponds to thenumber of magnets 104, where the number of sides of the channel 114 canbe adjusted to match the number of magnets 104 to be used. It is notedthat while FIG. 6 illustrates the channel 114 formed in portion 102 a,the channel 116 in the portion 102 b can have the same shape andpositioning. It is also noted that when the channels 114, 116 are notcircular, the magnet coupler portions 102 a, 102 b may be connectedtogether by means other than threaded surfaces 103, such as by usingpress fit, rabbiting, retaining rings or the like. The polygon shape forthe channels 114, 116 can help to reduce any air gap between thepoles/largest face of the magnets 104 and the magnet coupler 102,thereby increasing magnetic performance. In addition, this configurationenables the use of magnets 104 that are rectangular prisms, as comparedto for example curved magnets, which can be more expensive and difficultto manufacture.

The polygon of the channels 114, 116 can be regular or irregular, and inone case has at least four sides. However the polygon-shaped channel114, 116 can in some cases be difficult to machine. Thus if desiredchannels 114, 116 having a circular shape, which is easier to machine,can be used as shown in FIG. 7 , and used in conjunction withrectangular prism magnets 104. In this case the magnets 104 can bepositioned tangent to the channel 114, 116. Moreover, in this case themagnets 104 and/or channel 114, 116 can also be configured such thateach magnet 104 has three points of contact (or potential contact) withthe channel 114, 116: the center portions of each magnet 104 may be incontact or near contact with the radially-inner wall of the channel 114,116, and the circumferentially outer portions of each magnet 104 may bein contact or near contact with the radially-outer wall of the channel114, 116. The three points of contact (or near contact) helps tosecurely locate each magnet 104 in the channel 114, 116.

In order to position the magnets 104 in the channel 114, 116 it may notbe practical to provide three points of actual contact due to lack ofsufficiently precise manufacturing and lack of sufficient tolerances. Inthis case there may be a relatively small radially-extending outer gap122 between the circumferentially outer portions of the magnets 104 andthe radially-outer wall of the channel 114, 116, and/or between theinner/central surface of the magnets 104 and the radially-inner wall ofthe channel 114, 116. The gap(s) 122 for a given magnet 104 may have atotal cumulative length (in the radial direction) of less than about0.1″ in one case, or less than about 0.05″ in one case, or less thanabout 0.03″ in another case, or less than about 1% of the length of themagnet 104 (in a generally circumferential direction). The gap(s) 122may also be less than about 5% in one case, or less than about 1% inanother case, relative to a radius of an outer surface of the portion102 a/102 b.

Each magnet 104 may also define a somewhat triangular-shaped gap 124positioned between the circumferentially-outer portions of adjacentmagnets 104 and the radially inner surface of the channel 114, 116. Theinner gap 124 can be reduced as more magnets 104 are used. The gap(s)124 for a given magnet 104 can each, or cumulatively, have a length inthe radial direction that corresponds to the parameters of the gap 122outlined above.

The magnets 104 can also be positioned in various different arrangementssuch as that shown in FIG. 8 wherein the magnets 104, in end view, arepositioned in discrete, spaced apart, generally radially aligned closedchannels, in the same or similar manner as shown in the embodiment ofFIGS. 14, 15 and 15A and described in greater detail below.Alternatively, as shown in FIGS. 9-11 the magnets 104 can be positionedin channels 114, 116 that form various angles (defined by the anglebetween: a) a radially outwardly extending line aligned with the channel114, 116 and b) a radial line, as shown by the labelled angles in FIGS.9-11 ). Thus the plane defined by the largest faces of the magnets 104can be oriented perpendicular to a radial line (FIGS. 6 and 7 , whereinthe poles are aligned with a radial line), or parallel to radial line(FIG. 8 , wherein the poles are oriented perpendicular to a radial line)or positioned at various angles relative to a radial line (FIGS. 9-11 ).

Since each magnet 104 can be formed as a rectangular prism, each magnet104 may have a longest dimension (a length, in one case), that extendsor is oriented or aligned axially in the disclosed embodiment. Eachmagnet 104 may have a second-longest dimension (a width, in one case)that extends or is oriented or aligned radially (e.g. extends along aradial line) as in the embodiment of FIG. 8 ; or that extends or isoriented or aligned generally circumferentially as in the embodiments ofFIGS. 6 and 7 . Each magnet 104 may have a third-longest dimension(thickness) that extends or is oriented or aligned radially (e.g.extends along a radial line) as in the embodiment of FIGS. 6 and 7 . Inthis configuration the magnets 104 can also be considered to becircumferentially aligned.

In the embodiment of FIG. 11 the face of the magnets 104 with the northpoles 118 can be arranged to face radially inward, toward the centralaxis A of the assembly 42, which controls how the magnetic circuit iscompleted by forcing the magnetic field through the attraction member106. This arrangement of inwardly-facing north poles 118 may be utilizedwhen the magnets 104 are at an angle, relative to a radial line (on theradially outer side of the magnet 104 in one case), of equal to orgreater than 45 degrees as shown in FIG. 11 , and also FIGS. 6 and 7 .

In arrangements when the magnets 104 are arranged at angles equal to orless than 45 degrees (e.g. FIGS. 8-10 ) the polarity of the magnets 104,or the inwardly-facing surfaces of the magnets 104, can alternatebetween the north poles 118 and south poles 120. In these cases thepoles 118, 120 of the magnets 104 can alternate such that a north pole118 of each magnet 104 faces the north pole 118 of an adjacent magnet104. In addition, in these configurations an (exactly) even number ofmagnets 104 may be utilized to ensure the alternating pattern ismaintained about the entire circumference of the magnet unit 43. Thisalternating arrangement of magnets 104 (e.g. when arranged at angles ofequal to or less than 45 degrees) maximizes the magnetic flux field togenerate the highest level of available magnetic attractive force byphysically isolating the opposite poles 118, 120 of adjacent magnets 104to avoid a magnetic short-circuit between adjacent magnets 104.

The arrangement shown in FIGS. 8-10 (e.g. magnets 104 arranged at anglesof equal to or less than 45 degrees) can also reduce the adverse effectsfrom the repulsive forces between adjacent magnets 104. Such a repulsiveforce will occur when the magnetic field is flowing from north 118 tosouth poles 120 on a magnet 104, and the magnetic field from an adjacentmagnet 104 is flowing in the same direction. These magnetic interactionscan thereby be accommodated by the alternating pole arrangement to avoida reduction in the net magnetic attractive force, which as noted abovedefines or primarily determines the separation force between the magnetunit 43 and the attraction member 106.

If the magnets 104 are arranged at angles of equal to greater than about45 degrees (for example FIGS. 6 and 7 (90 degrees) and FIG. 11 (60degrees)), the number of magnets 104 can be even or odd, and themagnetic poles 118, 120 may not need to be alternated due to dissipatedmagnetic forces. In the embodiment of FIG. 11 the strength of themagnets 104 may need to be relatively low since the adjacent magnets 104may be more prone to a “short circuit” since the north poles 118 are notas physically isolated from the south poles 120 of an adjacent magnet104. In addition, the adjacent magnets 104 may experience greaterrepulsive forces since the poles 118/120 on one magnet 104 are not asphysically isolated from the poles 118/120 on an adjacent magnet 104.Thus in one case the magnets 104 are positioned at an angle other thanperpendicular relative to a radial line in axial end view. However, insome cases the embodiment of FIG. 11 , or other similar arrangementswhich do not provide optimized magnetic performance, may be desired whenthe magnetic force is desired to be somewhat lessened to adjust and finetune the separation force as desired. In addition, it should be notedthat other magnet arrangements are possible, some of which are describedin greater detail below.

In some cases magnet 104 which can be arcuate, and curve around thecenter A, in some cases matching the curvature of the curved channel114, 116. However in this case, because an arcuate magnet 104 is used,the inner surface defined by the inner diameter of the arced magnet 104will have a smaller surface area than the outer surface defined by theouter diameter of the arced magnet. The thicker the magnet 104, thelarger the difference in surface area.

As is well known, magnetic flux is the strength of the magnetic forcetimes the area around the pole. When arcuate magnets 104 are used, themagnetic flux on the inner surface of the arcuate magnets 104 is greaterthan the magnetic flux on the outer surface, since the surface area ofthe inner surface is smaller than the surface area of the outer surface.It is known that the number of magnetic force lines (magnetic field)from north to south must be the same for each magnet 104. With thesurface area of the inner surface being smaller than that of the outersurface for arcuate magnets 104, it follows that the flux density on theinner surface will be higher than that of the outer surface. The higherflux density results in a concentrated load on the inner surface of thearcuate magnets 104 that is higher than the load on the outer surface.Thus the use of arcuate magnets 104 provides a net total resultantmagnetic force that is lower than what is achievable under an optimizeddesign since the flux field entering the attraction member 106 has asmaller surface area than what is needed to effectively disperse anddistribute the magnetic flux field. This results in saturation of theportion of the attraction member 106, which causes underutilization ofthe total available magnetic field. It has been found that the largestimpact on magnet performance is the surface area of the face of themagnet 104 that is normal to the pole of the magnet 104.

In order to provide a balanced magnetic flux field, it may be desiredfor the inner annulus 108 of the magnet unit 43 to have an equalcross-sectional area, and/or equal volume, as the outer annulus 110.However, the inner annulus 108 can have a smaller diameter than that ofthe outer annulus 110. Thus as shown for example in FIGS. 2, 3 and 7 ,the inner annulus 108 of the magnet unit 43 can be thicker, in theradial direction, than the outer annulus 110, to provide an equalcross-sectional area and/or volume such that magnetic flux in the inner108 and outer 110 annuli are equal.

In some existing designs, the flux field around the ends of one magnet104 may be in the same direction as those of an adjacent magnet 104.These aligned flux forces produces a repelling force and can cause themagnets 104 to eject from the magnet unit 43, which can in turn causethe magnets 104 to be damaged or lost. The ejection force can also makeassembly and repair of the magnet unit 43 difficult, and can requirespecial processes and tools. Additionally, in some existing designs, asthe magnets 104 are installed, each magnets 104 is biased to shift awayfrom the adjacent magnet 104 due to the repelling magnetic fields. Thus,in this case the last few magnets 104 to be installed may require use ofa special tool to reach into the magnet coupler 102, and push the asidethe existing magnets 104 while installing the last few magnets 104.

The axial length of the channel 114, 116 (and/or the axial length ofeach magnet 104) can vary depending on the magnetic flux field desiredto be generated at the end of the magnet coupler 102. The channel 114,116 may have an axial length that is about equal to the axial length ofthe magnets 104 or slightly greater (within about 0.5% in one case, orabout 1% in another case, or within about 5% in another case) such thatthe channel 114, 116 closely axially receives the magnets 104 therein.In addition, the axial position of the channel 114, 116 can be adjustedas desired. For example in the embodiment of FIGS. 4 and 5 the upstreamportion 102 a of the magnet coupler 102, and its channel portion 114,can have the same axial length as the downstream portion 102 b and itschannel portion 116. In this case the channels 114, 116 and magnets 104are axially centered in the magnet coupler 102. In this scenario themagnetic force on each axial side of the magnet coupler 102 will be thesame (assuming other conditions that can effect magnetic force areidentical; for example, assuming the upstream 102 a and downstream 102 bportions are made of the same material, that their webs 112 have thesame thickness, etc.).

However if desired the magnet coupler 102/channels 114, 116 can beasymmetrical as shown in FIG. 12 such that one of the upstream 102 a ordownstream 102 b portions and/or their channels 114, 116 are longer thanthe other. In this case more of the length of the magnets 104 arereceived in one of the upstream 102 a or downstream 102 b portions. Forexample, in one case one of the upstream 102 a or downstream 102 bportions can have up to ⅞th of the axial length of the combined lengthof the channels 114, 116 and/or up to ⅞th of the axial length of themagnets 104 therein, and the other one of the upstream 102 a ordownstream 102 b portions can have the remaining (as little as ⅛th, inthe described embodiment) of the length of the combined channels 114,116 or magnets 104 therein. The upstream 102 a or downstream 102 bportion having the smaller portion of the magnets 104/channels 114, 116will have the weaker magnetic flux field compared to the other havingthe larger portion of the magnets 104/channels 114, 116.

The magnetic force on each axial side of the magnet coupler 102 can alsobe varied depending upon the method/mechanism used to join the upstream102 a and downstream 102 b portions of the magnet unit 43. In one casethe upstream 102 a and downstream 102 b portions are welded at the joint105 to form a welded joint therebetween, although care should be takenthat the heat from the welding process does not damage the magnets 104.In another case the upstream 102 a and downstream 102 b portions eachhave threaded surfaces 103 as noted above and are thus joined at thejoint 105 by a threaded connection, but could also be joined by avariety of other mechanisms/methods, such as press fit, rabbiting,retaining rings or the like.

The joint 105 in the magnet coupler 102 can cause a flux field leakage,which can vary depending upon the nature of the joint 105. For example,the magnetic flux field of the magnet coupler 102 can behave similar tofluids that want to travel the path of least resistance. The point offlux field leakage at the joint 105 of the magnet coupler 102 creates anarea of resistance, which aids in the division of the magnet field inthe magnet coupler 102. Thus, differing types of joints 105 will permitor block magnetic fields to pass therethrough by differing amounts.

For example, certain joints 105 may present a high flux field impedanceand block magnetic fields, and thus tend to magnetically isolate theupstream 102 a and downstream 102 b portions, which can provide greatercontrol over certain performance parameters. Other joints may have arelatively low flux field impedance to allow/transmit magnetic fieldsand thus tend to magnetically couple the upstream 102 a and downstream102 b portions, which can provide greater magnetic coupling strength andseparation force. If desired a gasket or other component can bepositioned in, at or adjacent to the joint 105 to provide a morepredictable control of the flux field impedance at the joint 105. Theuse of a gasket or component may be more practical when the upstream 102a and/or downstream 102 b portions are made from a paramagnetic ordiamagnetic material. The configuration and assembly of the magnetcoupler 102 can thus be varied to adjust the force generated at each endthereof to adjust the breakaway features and other magnetic performanceof the breakaway assembly 42.

In addition, the materials of the upstream 102 a and/or downstream 102 bportions of the magnet coupler 102 can be varied to adjust the magneticfield. For example, the upstream 102 a and downstream 102 b portions canbe made of various and different ferromagnetic metals or alloys thathave differing saturation points. The upstream 102 a or downstream 102 bportion that is made of material having a lower saturation point willgenerate a lower magnetic force. If only one side of the magnet coupler102 is desired to generate a magnetic force, then one of the portions102 a, 102 b can be made from a ferromagnetic material and the otherportion can be made of a paramagnetic or diamagnetic material, such as300 series stainless steel or 6000 grade of aluminum, and focus themagnetic flux at one end of the magnet coupler 102.

Magnets 104 can often be brittle and therefore it may be desired toposition such magnets 104 to avoid receiving direct impacts, ordissipating loads. The magnet unit 43 disclosed herein protects themagnets 104 when they are housed in the closed channels 114, 116 of themagnet coupler 102, and the magnets 104 are protected from directimpact. The closed channels 114, 116 allows the end surfaces of themagnets 104 to be recessed such that the attraction member 106 does notphysically engage or contact the magnets 104, but instead engages orcontacts the magnet coupler 102. In addition, the efficient design andlayout of the magnet unit 43 maximizes the use of the magnetic fluxfield and enables the magnet unit 43 to have a relatively smalldiameter, enabling the breakaway assembly 42 to have a smaller profile.

Another concern with magnets 104 is that they can be subject tocorrosion. In order to address this issue magnets 104 are often coatedor plated with various ferromagnetic metals, plastics or othermaterials. However, if these coatings are damaged the magnets 104 willbe prone to corrosion. Thus care must be taken during assembly andstorage of the breakaway assembly 42 to ensure the coating or plating ofthe magnets 104 is not damaged. The magnet coupler 102 helps to protectthe magnets 104 from corrosion by protecting them during theinstallation process and during use. The design provides a magnet unit43 with fully encapsulated magnets 104 that are sealed in an airtightand/or water-tight manner as a single sub-assembly that provides ease ofhandling and assembly, and provides protection to the encapsulatedmagnets 104.

Another issue that can arise is that magnets 104 may attract metalparticles and other items that are attracted to a magnetic field. Whensuch items or particles are positioned on the magnet 104 and/orattraction member 106, such items or particles can be trapped andimpacted when the attraction member 106 and magnet unit 43 engage eachother, thereby providing a pressure point that can damage or crack theattraction member 106 or magnet unit 43. However, in the current designthe magnets 104 are positioned in the closed channels 114, 116. Thus themagnets 104 are protected, and the end face of the magnet unit 43, whichcan be made of a more rugged material, can bear the brunt of suchimpacts. In some cases, the radially outer surface of the magnet coupler102 can be clad in aluminum or some other paramagnetic material to avoidcollecting metal from the ambient environment onto the magnet coupler102.

Some existing designs allow for direct exposure of the magnets to theatmospheric elements, which can lead to damage and/or corrosion. Inaddition some existing designs have inefficiencies in their magneticdesign in that certain portions of the magnetic field must pass throughsignificant areas of air and do not contribute to the magnetic force. Inaddition some designs distribute the magnetic flux field through anunduly large surface area due to the pattern of the magnets, decreasingthe effective strength of the magnetic field. In contrast, in the designdisclosed herein the magnets 104 can be fully encapsulated in the magnetcoupler 102, and thus the magnet coupler 102 protects the magnets 104from any corrosive material or debris. In addition, more magneticallyefficient design is utilized.

FIGS. 14, 15 and 15A illustrate one particular embodiment wherein themagnet coupler 102 has a plurality of radially-aligned channels 116,each of which closely receives a magnet 104 therein. In this case themagnets 104 are generally aligned along a radial line of the breakawayassembly 42. The magnets 104 can be arranged such that the poles 118,120 are in alternating directions as in the layout of FIG. 8 . Inaddition in the case shown in FIG. 15 there can be twelve channels116/magnets 104 that are spaced apart on center by 30 degrees. Eachmagnet 104 (and corresponding channels 114, 116) can have a thickness(extending, in the embodiment of FIG. 15 , generally in thecircumferential direction) of between about 0.025 inches 0.3 inches, andmore particularly between about 0.1 and about 0.2 inches in anothercase; a height (extending in the axial direction) of between about 0.2inches and about 1 inch, and more particularly between about 0.3 andabout 0.4 inches in another case; and a length (extending in the radialdirection) of between about 0.25 inches and about 2 inches, and moreparticularly between about 0.5 and about 1.25 inches in another case.The length and height dimensions described above may be reversed ifdesires. These dimensions of the magnets 104 and channels 114, 116 canalso apply to the other embodiments described herein, regardless oforientation.

In the embodiment of FIGS. 14, 15 and 15A, the magnet unit 43 mayinclude a magnet retainer 117, as best shown in FIG. 15A, can be used tosecure the magnets 104 in the desired position and orientation. Inparticular the magnet retainer 117 can include a base ring 119 (whichcan be analogous to and/or define the web 112) and a plurality ofgenerally wedge-shaped spacers 121 coupled to and extending axially awayfrom the ring 119. The spacers 121 define the generally rectangularprism-shaped channels 116 in which the magnets 104 are received. Themagnet unit 43 may include a retaining ring 123 (FIG. 14 ) received in acorresponding recess downstream of the magnet retainer 117 to keep themagnet retainer 117 and magnets 104 in place.

In this embodiment the magnet retainer 117 can be made of the samematerials, such as ferromagnetic materials, as the attraction member 106outlined above, and in one case is made of a magnetizable material. Inthis case the base ring 119 of the magnet retainer 117 can act as ashunting member, analogous to the web or end wall 112 of the embodimentof FIGS. 2-4 , and the spacers 121 can become magnetized by the adjacentmagnets 104. Although the magnet retainer 117 is shown in conjunctionwith the embodiment of FIGS. 14 and 15 , it should be understood thatthe magnet retainer 117 can be used in other configurations, in place ofthe magnet coupler 102 if desired.

As outlined above the coupling mechanism 41, including the magnet unit43 and the attraction member 106, provide the sole or primary separationforce to the breakaway assembly 42. Starting in the coupled position, asshown in FIG. 2 , the connectors 44, 46 are held together by theattractive force between the magnet unit 43 and the attraction member106. This attractive force can be at a minimum of 100 lbs. as per thecurrently applicable U.S. standards/regulations, but can be set atvarious other levels as desired. Thus use of magnets, along with thevarious adjustment factors described above, helps to ensure that theseparation force of the breakaway assembly 42 is reliable andpredictable, with relatively small variances between differingassemblies 42. In one case the force required to separate the first 44and second 46 connectors is in one case at least about 50 lbs., or inanother case at least about 80 lbs. or in another case at least about100 lbs., or in another case at least about 150 lbs., or in another casebetween about 80 lbs. and about 150 lbs., or at least about 300 lbs. inyet another case, or less than about 500 lbs. in one case, or less thanabout 300 lbs. in yet another case.

When it is desired to reconnect the breakaway assembly 42, theconnectors 44, 46 can be pressed together in the axial direction, withthe stems 84, 62 engaging each other and then opening the associatedpoppet valves 80, 54. When sufficient force is applied the magnet unit43 is positioned sufficiently close to the attraction member 106 thatthe attractive force between those components overcomes the repulsiveforce applied by the springs 94, 74, and the breakaway assembly 42 isretained in the open position shown in FIG. 2 .

Force Spike Accommodation—Spring

The fluid in the fluid path 32 can sometimes experience pressure spikes,pressure shocks or line shocks due to uneven operation of the pump 24,pressure imposed by operation of the user, or by other forces which maybe relatively short in duration and tend to cause undesired separation(collectively termed a force spike herein). For example, in conventionalfuel systems force spikes can be caused by a shut-off valve in thenozzle 18 closing the fluid path 32, while the pump 24 continues tooperate for short period of time. Force spikes can also be caused by theuser jerking on the hose 16, or from other sources. In many pressurespikes situations, the pressure spike has relatively low energy and maydissipate as it travels through the fluid path, since the fluid may beconsidered to be incompressible and have a relatively high energytransfer rate. However in this case the pressure spike may be presentover a relatively long time period.

In some existing systems the force spike can apply a force to the poppetvalve 54 of the downstream connector 46 or other components of thedownstream connector 46. In existing single use breakaways, theconnecting member that connects the upstream 44 and downstream 46connectors can be relatively rigid and can shear or break when asufficient force spike force is applied, causing an undesiredseparation. Some reconnectable breakaways are better at handling impulseloads generated from, for example, a user jerking on the hose 16, but asufficiently high force by user force can still cause separation.Reconectable breakaways that use compression or canted coil springs maylack sufficient response time; e.g. may not be able to transmit the loadthrough the coils in sufficient time, which can lead to damage to thecompression or canted coil spring.

The breakaway assembly 42 illustrated in for example FIGS. 2 and 13 isconfigured to accommodate force spikes without causing damage to thecomponents and without undue undesired separation. In particular,upstream connector 44 can include an inner member 129 (e.g. defined inone case by portions of the upstream connector 44 other than the magnetunit 43) that has a limited range of axial movement or “float” relativeto the magnet unit 43 to allow the assembly 42 to accommodate some forcespikes without causing undesired separation events. The inner member 129can be an annular component that extends entirely circumferentiallyaround the fluid path 32. The magnet unit 43 can thus be considered tobe movably mounted within the upstream connector 44, which enables theassembly 42 to accommodate force spikes in the system without causingseparation.

In particular, the magnet unit 43/magnet coupler 102 can have agenerally annular skirt 126, which can be part of or integral with thebody of the magnet coupler 102. The skirt 126 is positioned upstream ofthe magnets 104, defining a shoulder 128 and an annular recess 130positioned upstream of the shoulder 128. An annular retaining ring 132is positioned in the recess 130. The magnet unit 43 further includes aretaining washer 134 positioned adjacent to, and axially downstreamfrom, the retaining ring 132.

The inner member 129 has a lip 136 positioned adjacent to, and axiallyspaced apart from, the retaining washer 134 when the assembly 42 is inthe position shown in FIG. 2 . A first gap 137 is positioned between thelip 136 and the retaining washer 134 during normal operating conditions.A biasing element or resilient component 138 is positioned in a recessof the inner member 129 and can be in compression and engaging both theinner member 129 and the retaining washer 134, and can include or takethe form of a wire wave spring or other spring or resilient memberhaving a predetermined preload. The resilient component 138 biases theinner member 129 to its rest or axial inner position, shown in FIG. 1 ,and can be fluidly isolated from the fluid path 32.

When a pressure spike propagates through the fluid path 32 and/or animpulse load is applied (e.g. by a user) the applied force can cause theinner member 129 and the poppet valve 80 of the upstream connector 44(carried therewith) to move axially away from the magnet unit 43 andupstream connector 44. As shown in FIGS. 13 and 13A in one case therelative movement can appear as the inner member 129 and poppet valve 80moving upstream, as compared to FIG. 2 , to an actuated or axial outerposition. The inner member 129 can move upstream in a relative directionuntil the lip 136 of the inner member 129 engages the retaining washer134, thereby eliminating the first gap 137 of FIG. 2 , while introducinga second gap 140 as shown in FIGS. 13 and 13A between the shoulder 128and the downstream face of the inner member 129. The magnet unit 43 andthe attraction member 106 remain magnetically coupled during suchforce-spike induced movement, and the full stroke of the force-spikeaccommodating movement is defined by the first gap 137 of FIG. 2 , whichgap 137 is eliminated in FIG. 13 during full movement of the innermember 129. Of course, the inner member 129 does not necessarily need tomove a full stroke to accommodate force spikes, and the gap 137 will insuch cases be reduced/narrowed but not necessarily eliminated. In themanner the upstream connector 44 can have a gap introduced therein toaccommodate force spikes, while the upstream 44 and downstream 46connectors remain coupled.

If the force spike overcomes the resistance of the resilient component138, then the inner member 129/assembly 42 will shift axially out, up toa fixed distance, to its force-spike accommodating position shown inFIG. 13 . The associated poppet valve 80 remains open and does not shiftto its closed position, even when the inner member 129 is in itsforce-spike accommodating position. The inner member 129 can move to itsforce-accommodating position, while the remaining portion of theconnector 44 and/or the other connector 46 remain relatively fixed.Since the spike forces are typically a quick pulse, once the innermember 129 shifts to the pressure-spike or force-spike accommodatingposition and the force spike has sufficiently diminished, the resilientcomponent 138 will quickly urge the assembly 42 back to its positionshown in FIG. 2 , wherein the downstream face of the inner member 129engages and is pressed against the shoulder 128 of the magnet unit 43.It should be noted that, when in the force-spike accommodating positionshown in FIG. 13 , a sufficient separation force, applied eitherexternally or by a sufficiently high pressure spike or combinationsthereof, will still cause the magnet unit 43/upstream connector 44 toseparate from the attraction member 106/downstream connector 46 in aseparation event as described above.

The assembly 42 can accommodate force spikes that propagate in both theupstream direction and the downstream direction. In particular, bothsuch force spikes can cause the same relative movement of the assemblyfrom its rest position of FIG. 2 , as shown in FIGS. 13 and 13A. Thusthe resilient component 138 can accommodate and absorb the pressure orspike force in either direction. In addition, when a user jerks on thehose 16, applying a direct physical force that tends to want to separatethe assembly 42, the resilient component 138 can help to absorb suchforces and reduce breakaway events.

The resilient component 138 will have a predetermined preload force andcompression point load. The resilient component 138 and maximum size ofthe gap 140 will both limit the stroke of the inner member 129 to apredetermined distance to ensure that the seal 47 on the upstream outercircumferential end of the downstream connector 46 is not pulled out ofthe bore, or out of contact with, of the inner surface of the upstreamconnector 44 when the assembly 42 is in its force-spike accommodatingposition. Thus the maximum stroke distance (e.g. axial dimension of thegap 137 and/or gap 140, possibly shortened by the compressed length ofthe resilient component 138) may be relatively short, such as less thanabout 5/16″ in one case, or less than about ¼″ in another case, or lessthan about ⅛″ in another case, or less than or equal to about 1/16″ inanother case, and greater than about 1/32″ in yet another case.

The force required to cause the assembly 42 to move to its force-spikeaccommodating position may be set to a lower value than the separationforce. For example, if the separation force is set to 250 lbs., then theforce required to cause the assembly 42 to move to its force-spikeaccommodating position can be set at a value less than 250 lbs., forexample about 175 lbs. in one case. The assembly 42 may be able toaccommodate various levels of force spikes, that are less than theseparation force, such at least about 40 lbs. in one case, or at leastabout 60 lbs. in another case, or at least about 80 lbs. in yet anothercase, or greater than about 25% of the separation force in one case, orgreater than about 50% of the separation force in another case, or lessthan the separation force in one case, or less than about 90% of theseparation force in yet another case. The force required to induceforce-spike accommodation should be high enough to accommodatemeaningful force spikes, but not so high as to risk being ineffectiveand effectively overridden by a breakaway event, and not so low as toenable frequent force-spike accommodation which can cause fatigue of thevarious components that accommodate force spikes.

In such a force spike event, the energy of the force spike is absorbedby the resilient component 138. This accommodation of force spikesreduces unintended separations and improves the fuel dispensingexperience. In addition, allowing the inner member 129 to move/floatrelative to the remainder of the upstream connector 44 isolates thejoint 105 of the magnet coupler 102 from fluid spike forces. Instead ofapplying forces to the joint 105, the spike forces are applied toannular areas, such as the retainer washer 134, retaining ring 132, andrecess 130 of the assembly 42, which can be designed and configured toaccommodate applied loads.

In addition or in the alternative, instead of having the magnet unit 43move or “float” to accommodate force spikes, the attraction member 106can instead be configured to “float” in the downstream connector 46 suchthat the downstream connector 46 can accommodate force spikes in eitherdirection. In this embodiment, the resilient component 138 (andretaining ring 132 and retaining washer 134, if desired) are positionedadjacent to the attraction member 106 (e.g. in gap 113 in one case) inmanners which are apparent to a person of ordinary skill in the art astaught by the illustrated embodiments in FIGS. 2 and 13 . In this case,when there is a force spike in the fluid path 32, the attraction member106 may move slightly relatively axially, such as downstream, and theassociated resilient component 138 is compressed, absorbing the force ofthe force spike. Once the force spike is dissipated, the attractionmember 106 returns to its original position as biased by thespring/resilient member 138.

As outlined above the magnet unit 43 and/or attraction member 106 canuse springs or other energy-absorbing devices to accommodate forcespikes in the system. In the case where both the magnet unit 43 andattraction member 106 are configured to accommodate force spikes, theforce-spike accommodation system can be arranged to accommodate forcespikes in a staged manner. For example, the resilient components 138 canhave different spring constants or otherwise be arranged to be activatedat different levels of force. In this case one of the force-spikeaccommodation systems can be activated at a lower pressure or force, andthe other one of the force-spike accommodation systems can be activatedat a higher pressure or force. In one case the higher force-spikeaccommodation system can be configured to be activated just as the lowerforce-spike accommodation system reaches its limit; that is in one caseas or just before the gap 137 is eliminated. Such a “double floating”system can thereby bracket spike forces and accommodate them in a moreefficient manner, and provide the ability the accommodate more powerfulforce spikes.

It should be further understood that the force spike accommodationsystem, while shown herein in conjunction with a magnetic couplingsystem 41, is not necessarily limited to use with such a magneticcoupling system 41. Instead the force spike accommodation system andfeatures can be used with nearly any system or component for couplingthe first 44 and second 46 connectors, including mechanical couplingsystems.

Force Spike Accommodation—Magnetic

In a further alternative embodiment for accommodating force spikes,rather than using the resilient component 138, as shown, in one case, inFIG. 16 a magnetizable material 142 can be coupled (e.g. by aschematically-shown threaded joint 144 in one case, but various othercoupling mechanisms can be used) to the inner member 129 of the upstreamconnector 44, and the magnets 104 can act as a biasing element to aid inaccommodating force spikes. The magnetizable material 142 is positionedadjacent to, but not directly coupled to, the shoulder 128 of the magnetunit 43/magnetic coupler 102. The magnetizable material 142 can be forexample a ferromagnetic alloy member having a saturation point greaterthan 1.25 Tesla. The magnetizable material 142 can be magneticallyattracted to the magnets 104/magnet unit 43 (with a force lower than theseparation force) to allow floating of the magnet unit 43 to accommodateline shock or pressure shock as described above. When a line shock,impulse load or force spike of sufficient force is experienced in theembodiment of FIG. 16 , the inner member 129 will move relativelyupstream (and/or the connector 46 will move relatively downstream),narrowing or closing the gap 137, while another gap 140 (FIG. 16A) opensbetween the magnetizable material 142 and the shoulder 128.

When a magnetic force is used to control and accommodate force spikes asper the embodiment of FIG. 16 for example, one end (e.g. the upstreamend) of the magnet unit 43 may be desired to have a lower magnetic forcethan the other end (e.g. the downstream end) to ensure the forcerequired to cause the assembly 42 to move the assembly 42 to itsforce-spike accommodating position (FIG. 16A) is lower than theseparation force. This can be accomplished in some of the mannersoutlined above, such as the having the downstream portion 102 b of themagnetic coupler 102 being made of a material having a higher saturationpoint then the upstream portion 102 a, thus increasing its efficiencyand separation force, or by use of a gasket at the joint 105, by varyingposition of the magnets 104 in the magnet coupler 102, by increasing thethickness of the web, etc. In one case the one of the portions 102 a/102b (the downstream portion 102 b in one case) of the magnetic coupler 102can be made of a material having a saturation point of greater than 1.25Tesla, and the other portion 102 a/102 b (the upstream portion 102 a)can be made of a material having a saturation point of less than 1.25Tesla, or be made of a paramagnetic or diamagnetic alloy or material. Inthe case where a spring or other resilient component 138 is used toaccommodate force or pressure spikes, the upstream portion 102 a of themagnetic coupler 102 can be made of a paramagnetic or diamagneticmaterial, since a magnetic field may not be needed on the upstream sideof the magnet coupler 102.

Another way to provide a reduced magnetic force on the upstream end ofthe magnet unit 43/magnetic coupler 102 would be to simply increase thethickness of the web 146 (e.g. the axially extending thickness at theupstream end) of the upstream portion 102 a, which shunts the magneticflux to reduce the magnetic force to the desired level. However it hasbeen found that if the web thickness 146 is made too great (greater thanabout ¼″ in one case) the attraction force may be lowered too much, andthus may not be practical. On the other hand, if the web thickness 146is too small (less than about 1/64″ in one case) the strength/integrityof the magnet unit 43 may be compromised. Another way to provide areduced magnetic force on the upstream end of the magnet unit 43 wouldbe to reduce the diameter of the magnet unit 43, which reduces magneticefficiency.

It should also be understood that the magnetic-based system fordissipating force spikes (FIGS. 16 and 16A) can be used in combinationwith the spring-based system for dissipating force spikes (FIGS. 1, 12,13 and 15 ) to provide two separate systems, usable together, foraccommodating force spikes, acting either on the same components, or ondifferent components to provide staged force spike accommodation asoutlined above. It should also be noted that the magnetic pressuredissipation system can also be used in the downstream connector 46, withcorresponding structure to that described above being provided andadjusted as needed.

Thus, it can be seen that when the magnet unit 43 is used to accommodateforce spikes, the magnet unit 43 serves a dual purpose in controllingthe separation force and also controlling the force-spike accommodationforce. Accordingly the magnet unit 43 provides a usable magnetic fieldon both axial ends thereof, where the relative strength of the magneticfield on each end can be controlled as desired. Alternatively the magnetunit 43 may provide a usable magnetic field on only one end thereof

Relatively Higher-Pressurized Safety Breakaway

The breakaway assembly 42 described above is generally designed for usewith convention fuels, such as gasoline, diesel, etc. that are notstored and/or delivered under significant pressures. However themagnetic breakaway design and/or similar or analogous structures canalso be used in systems that store and deliver fuel or fluid underrelatively high pressure, such as CNG, hydrogen, LPG or the like. Inthese cases the fuel can be stored and dispensed under pressure (in onecase in the range of between about 70 psi and about 10,000 psi, and inanother case between about 2,900 psi and about 3,600 psi, or at leastabout 70 psi in one case, of at least about 150 psi in one case, or atleast about 2,000 psi in another case, or in another case at least about2,900 psi, or less than about 3,600 psi in one case, or less than about10,000 psi in another case).

The breakaway assembly 42′ shown in FIGS. 17-22 is somewhat analogous tothose shown in FIGS. 2-16 , with the same reference numbers (either withor without a “prime” indicator and/or a letter indicator in certaincases) used for the same or analogous components, although the flowdirection in the drawings of FIGS. 17-22 is opposite to that of theFIGS. 2-16 embodiment. Thus for example the breakaway assembly 42′ ofFIGS. 17-22 includes the first or upstream connector 44′ and the secondor downstream connector 46′, and fluid to be dispensed flows in aleft-to-right direction. The first connector 44′ includes a connectionstructure 147 having a series of generally axially-extending,circumferentially spaced flanges or jaws 148 that can releasably engagea circumferentially extending recess/ramp 150 on the second connector46′, as will be described in greater detail below. The second connector46′ has a neck portion 154 which carries the recess 150 on a radiallyouter surface thereof, and a fixed shaft member 153 is positioned in thesecond connector 46′. The shaft member 153 has an inner cavity 155thereon and facing upstream. A poppet valve 80′ is positioned in thesecond connector 46′. A valve 151, such as a curtain valve havingcurtain valve member, shuttle valve, closure valve or slider 152 ismovably positioned in the first connector 44′, and movable between anupstream/open position, shown in FIG. 17 , and a downstream/closedposition, shown in FIGS. 18 and 19 .

The first connector 44′ includes a center shaft or tubular structure 158about which the slider 152 is movably/slidably mounted. The slider 152includes an annular sealing structure 156 that closely fits about thecenter shaft 158. The center shaft 158 can be hollow, having a centralcavity 160 therein and a plurality of radially-extending openings 162(or at least partially radially-extending openings 162 which can extendprimarily radially, or form an average angle of greater than 45 degreesrelative to a central axis in one case, or greater than 65 degrees inanother case, or strictly radially extending in yet another case) whichform part of the fluid path 32, positioned adjacent to a downstream endthereof, that are in fluid communication with the cavity 160. The firstconnector 44′ has a pair of seals 164, 166 positioned on the centershaft 158. The upstream seal 164 is positioned upstream of the openings162, and the downstream seal 166 is positioned downstream of theopenings 162.

When the assembly 42′ is in its connected configuration, as shown inFIG. 17 , the downstream end of the center shaft 158 is received in theinner cavity 155 of the shaft member 153. In this position thedownstream seal 166 of the first connector 44′ engages the radiallyinner surface of the shaft member 153 (e.g. the radially outer surfaceof the inner cavity 155) and the upstream seal 164 of the firstconnector 44′ engages the radially inner surface of the distal end ofthe neck portion 154, to seal the fluid in the fluid path 32 as fluidflows from the upstream connector 44′ to the downstream connector 46′ asshown by the arrows in FIG. 17 .

In this manner fluid can flow down the cavity 160 of the center shaft158, radially outwardly through the openings 162 and encounter thepoppet valve 80′. The poppet valve 80′ includes a movable member 168having a sealing surface 170, and is biased to an upstream/sealingposition by spring 94′. When the poppet valve 80′ is closed its sealingsurface 170 sealingly engages valve seat 172 on the shaft portion 53, asshown in FIGS. 18 and 19 . In contrast, when fluid of sufficientpressure acts on the poppet valve 80′, the movable member 168 movesdownstream, compressing the spring 94′, and allowing fluid to flow pastthe poppet valve 80′ as shown in FIG. 17 . Thus when the assembly 42′ isin the configuration shown in FIG. 17 , under sufficient pressure fluidcan flow to the nozzle 18 in the direction of the arrows shown in FIG.17 .

When an axial separation force is applied to the first 44′ and second46′ connectors, the slider 152 moves to a downstream position (in amanner which will be described in greater detail below), as shown inFIG. 18 . In this position the sealing structure 156 of the slider 152extends over, and sealingly engages/covers, the openings 162 of thecenter shaft 158, and thus blocks fluid flow as or in the manner of acurtain valve. The sealing structure 156 of the slider 152simultaneously sealingly engages both seals 164, 166 of the upstreamconnector 44′ to provide a secure seal. When first 44′ and second 46′connectors are properly and fully reconnected, the slider 152 isretracted or moved upstream (in a manner which will be described ingreater detail below), and the openings 162 are uncovered such thatfluid can flow through the assembly 42′.

As noted above, the connection structure 147 can include a plurality ofaxially-extending flanges 148 on the first connector 44′, wherein eachflange 148 is circumferentially spaced from any adjacent flanges 148.Each flange 148 may be movable or pivotable in the radial direction(e.g. be moved radially outwardly from the position shown in FIG. 17 tothe position shown in FIGS. 18 and 19 ). Each flange 148 may be biasedto be in its radially outward positions shown in FIGS. 18 and 19 , by aspring 182 or the like that extends circumferentially around the baseends of the flanges 148 and urges the flanges 148 radially outwardly bya lever force, pivoting about pivot location 188. Each flange 148 mayalso be axially coupled to and axially movable with the slider 152.

When the slider 152/connection structure 147 is in its upstream positionor first axial position, as shown in FIG. 17 , the downstream ends ofthe flanges 148 are positioned radially inside the attraction member 106b and prevented from moving radially outward. This means that theflanges 148 are positioned in the recess 150 and securely grip thedownstream connector 46′, preventing separation. In contrast, when theslider 152/connection structure moves to its downstream or second axialposition, as shown in FIG. 18 the downstream end of the flanges 148protrudes axially beyond the attraction member 106, enabling the flanges148 to move radially outwardly, out of the recess 150 and therebyrelease the downstream connector 46′. In this manner, the slider 152 canbe positively axially coupled to the downstream connector 46′ when theassembly 42′ is in the coupled configuration, and the slider or closurevalve 152 is released and not axially coupled to the downstreamconnector 46′ when the assembly 42′ is in the disconnectedconfiguration. In other words the downstream connector 46′ can beconfigured to move the slider or closure valve 152 to the closedposition when the assembly 42′ moves from the connected configuration tothe disconnected configuration.

Each flange 148 may include a surface 180 that is angled (i.e. extendingat a non-parallel angle relative to the central axis) on its radiallyinner surface. The upstream connector 46′ may include a ramp or angledsurface 190 that engages the ramp or angled surfaces 180 when the slider152 is in its upstream position as shown in FIG. 17 . When the slider152 slides to its downstream position, as shown in FIGS. 18 and 19 , theangled surfaces 180/190 slide axially relative to each other, and theflanges 148 are thereby positively moved to their radially outerposition, releasing the downstream connector 46′. In contrast, when theslider 152 moves returns to its upstream position (e.g. moving from theposition of FIGS. 18 /19 to the position of FIG. 17 ), angled surfaces191 on the radially outer surfaces of the flanges 148 engage an angledsurface 193 on the attraction member 106 b to positively move theflanges 148 to their radially inner position. However it should beunderstood that the connection structure 147 can take any of a widevariety of other forms or mechanisms for releasably coupling the slider152 and the downstream connector 46′, such as various ramps,interengaging fingers, interengaging geometry, magnetic couplings,spring connections, etc.

A coupling mechanism 41′ can be used to secure the slider 152 in itsupstream position and thereby axially secure the upstream 44′ anddownstream 46′ connectors, and to solely or primarily supply theseparation force to the breakaway assembly 42′. The coupling mechanism41′ can include a magnet unit 43′ that is coupled to or forms part ofthe slider 152 that is the same as or analogous to the magnet unit 43′described above. However in this case the magnet unit 43′ is coupled tothe slider 152 and movable with the slider 152 as will be described ingreater detail below. In addition, the assembly 42′ can include a pairof attraction members 106 a, 106 b that are the same as or analogous tothe attraction member 106 outlined above. In particular, the attractionmember 106 a of the embodiment of FIGS. 17-22 is positioned at anupstream end of the upstream connector 44′, and magnetically engages themagnet unit 43′/slider 152 when the magnet unit 43′/slider 152 is in itsupstream position to provide the separation force. In addition, theupstream attraction member 106 a may axially float in the system suchthat the attraction member 106 a is axially movable, but constrained insuch movement in both axial directions by a fixed body 111 and retainingwasher 134, respectively. The attraction member 106 a may be biased inthe upstream direction by spring or resilient element 138.

The attraction member 106 b is positioned at a downstream end of theupstream connector 44′, and magnetically engages the magnet unit43′/slider 152 when the magnet unit 43′/slider 152 is in its downstreamposition, to provide a desired reconnection force. The magnet unit 43′can be magnetically attracted to the attraction members 106 a, 106 b,and by the same or variable amounts by for example adjusting theproperties of the magnet unit 43′ and/or attractions members 106 a, 106b as outlined above. In one embodiment, the attraction of the magnetunit 43′ to the downstream attraction member 106 b (when the slider 152is in its downstream position) is greater than the attraction of themagnet unit 43′ to the upstream attraction member 106 a (when the slider152 is in its upstream position). Thus in this case the reconnectionforce of the assembly 42′ may be greater than the separation force. Thiscan provide a safety feature as described in greater detail below.

When the assembly 42′ is in the fully connected configuration shown inFIG. 17 , the slider 152 is in its upstream position, and held inposition due to magnetic engagement between the magnet unit 43′ and theattraction member 106 a. During a breakaway event, a downstream axialforce is applied to the second connector 46′, which is transmitted tothe slider 152 due to the engagement of the ramp 190 of neck portion 154and the angled surfaces 180 of the flanges 148. Accordingly, an appliedseparation force is applied to, and must first overcome, the magneticattraction between the magnet unit 43′ and the upstream attractionmember 106 a, which causes the slider 152 to move to its downstreamposition shown in FIG. 18 . As the slider 152 moves to its downstreamposition the distal end of the flanges 148 move axially clear of theattraction member 106 b, which enables the flanges 148 to move to theirradially outward position as biased by the spring 182. This, in turn,causes the flanges 148 to release the downstream connector 46′, and theslider 152 fully moves to its downstream position.

When the downstream connector 46′ is separated from the upstreamconnector 44′, the downstream connector 46′ imparts a downstream forceto the slider 152, thereby securely pulling the slider 152 into itsclosed position to seal the openings 162 by the seals 164, 166 asdescribed above. In addition since the slider 152 is moving downstream,the force of the pressurized fluid upstream of the slider 152 urges theslider 152 to its closed position thereby providing a reliable seal. Asthe downstream connector 46′ separates from the upstream connector 44′the poppet valve 80′ in the downstream connector 46′ is closed as biasedby its spring 94, which can overcome the reduced pressure in the fluidpath 32 due to closure of the openings 162. Thus, after a separationevent both connectors 44′, 46′ can be fluidly sealed in a reliablemanner.

In order the couple the connectors 44′, 46′ and move the assembly 42′ toits connected configuration, the connectors 44′, 46′ may begin in anaxially-spaced apart position, as shown in FIGS. 19 and 21 . Theconnectors 44′, 46′ are then axially moved together and the secondconnector 46′ engages the slider 152 (FIG. 18 ) and moves the slider 152upstream (uncovering the openings 162 and opening the valve 151) untilthe magnet unit 43 engages the upstream attraction member 106 a. Oncethe second connector 46′ is sufficiently axially inserted, the flanges148 are moved radially inwardly by the angled surfaces 191, placing thespring 182 in tension. The flanges 148 then engage the ramp 190 and arereceived in the recess 150 to secure the connectors 44′, 46′ together.Once the connectors 44′, 46′ are connected and the curtain valve 151 isopen, pressurized fluid flows into the downstream connector 46′ andopens the poppet valve 80′ therein due to the pressure exerted by thefluid on the poppet valve 80′, as shown in FIG. 17 .

In order to move the assembly 42′ from its disconnected configuration ofFIG. 19 to its connected configuration of FIG. 17 , in one case areconnection tool 202 as shown in FIGS. 21 and 22 may be utilized. Theconnection tool 202 includes a pair of manually operable handles 204that are operable coupled, via various linkages and pivot connections,to a first coupler 206 and a second coupler 208. The first coupler 206is a generally annular component configured to closely fit in a recess210 on an outer surface of the first connector 44′. The second coupler208 is a generally annular component configured to fit over a lip 212 ofthe second connector 46′.

When the connection tool 202 is in the configuration shown in FIG. 21 ,and the handles 204 are oriented in a radial direction the first coupler206 and second coupler 208 are relatively axially spaced apart. Theconnection tool 202 is then operated such that the handles 204 arepivoted about their pivot points 203 until they handles 204 are orientedin an axial direction, and the first coupler 206 and second coupler 208are moved axially closer together, as shown in FIG. 22 , thereby pullingthe second connector 46′ into the first connector 44′ as outlined above.In some cases the tool 202 may be provided to only certified trainedpersonnel to ensure the connection and reconnection process is completedproperly and that the system is properly inspected before and afterseparation.

When the slider 152 is in its downstream position (FIGS. 18 and 19 ),the magnet unit 43′ magnetically interacts with, and is thusmagnetically coupled to, the downstream attraction member 106 b. Thedownstream attraction member 106 b thus acts as a security measure tolock the slider 152/curtain valve 151 in its closed position, andrequires a predetermined force to move the slider 152 away from thedownstream position. In particular, the magnet unit 43′ and attractionmember 106 b together ensure that a sufficiently high force is requiredto return the slider 152/curtain valve 151 to its open position so thatonly authorized/sufficiently trained personnel can reconnect theassembly 42′. This can help to ensure that the assembly 42′ is properlyassembled and that the parts are in good working order. In one case, theforce required to move the slider 152/curtain valve 151 away from itsdownstream position is about 200 lbs., or greater than the separationforce in one case, or greater than about 25% the separation force in onecase, or less than the separation force in one case, or less than about50% of the separation force in another case. However, the inclusion ofthe attraction member 106 b is optional and the attraction member 106 bcan be omitted if desired.

In some cases, the downstream connector 46′ may include a vent 200 (FIG.19 ) in the form of a relatively small opening that provides fluidcommunication between the fluid path inside the downstream connector 46′(downstream of the poppet valve 80′) and the ambient atmosphere. In thiscase after a separation event when the poppet valve 80′ of thedownstream connector 46 is closed, the vent 200 allows for a controllerrelease of fluid that may be trapped by the poppet valve 80′ to reducepressure in the system.

The assembly 42′ of FIGS. 17-22 provides a robust and reliable shut-offvalve in which the sealing functionality is provided by the sealingstructure 156 of the slider 152 extending over and sealing the openings162 of the center shaft 158. In this case the sealing surfaces areentirely positioned inside the assembly 42′ in both the connected andunconnected states of the assembly 42′ and protected from externalforces, and from dirt/debris. The slider 152/curtain valve 151 allowsflow or shuts off flow from radially outside the fluid path 32/cavity160, as the slider 152 seals on the outer surface/diameter of the centershaft 158. The existence of pressure in the cavity 160 of the centershaft 158, when the slider 152/curtain valve 151 is closed, exerts aforce radially outwardly. However the slider 152/curtain valve 151 ismoveable axially between its open and closed positions. Thus theexistence of radially exerted pressure in the cavity 160/center shaft158 does not affect operation of the slider 152/curtain valve 151, andthe curtain valve 151 is thereby pressure balanced when the slider 152is in its downstream/closed position, and the pressure of the fluid doesnot tend to either open or close the curtain valve 151. In this case anexternal force is required to open or close the slider 152/curtain valve151. In addition, when the slider 152 is in its downstream position bothseals 164, 166 engage the slider 152 to thereby trap/close the openings162 for a strong seal. The curtain valve 151 thus reduces susceptibilityto force spikes, although the assembly 42′ can include force-spikeaccommodation features as will be described below.

As noted above, the seals 164, 166 are captured and internallypositioned so that they resist removal. In contrast, in certain otherdesigns the seals can be blown out of position during a separationevent, and the person who reconnects the assembly may not notice themissing seals. However, the present design minimizes the chance fordisplacement of the seals 164, 166. Moreover, the angled surfaces 180 onthe flanges 148 that axially connects the two connectors 44′, 46′ facesradially inwardly and are protected from damages. The correspondingangled ramp 190 faces radially outwardly but is also protected fromdamage when the assembly 42′ is in its connected configuration, and inaddition the ramp 190 is easily visible for inspection after aseparation event to ensure the ramp 190 is not damaged.

In addition, the magnet unit 43′ is directly coupled to the slider152/curtain valve 151, which provides a quicker response in terminatingthe flow of fluid. Many current systems rely on pressure, flow and abiasing spring to close a check valve or the like. In those cases, ifthere is any debris in the fluid path 32 the valve can be held openand/or slow to close. In contrast, the assembly 42′ has no or littlesurfaces (e.g. surfaces that are perpendicular to the direction of theflow) that debris can collect on to prevent the valve 151 from closing,since the slider 152 is slidably positioned on, and slides axially over,the center shaft 158. In addition any debris positioned on the centershaft 158 can be displaced and cleaned away by axial sliding of theslider 152 to provide a self-cleaning design.

The assembly 42′ and in particular the slider 152/curtain valve 151design provides a component in which, when the assembly 42′ is in itsconnected configuration, a relatively low number of parts in theupstream connector 44′ are exposed to pressure; e.g. the slider 152,both seals 164, 166, the upstream threaded adapter 48, the center shaft158 and internal components of the downstream connector 46′. After aseparation event, when the curtain valve 151 is closed, the onlycomponents of upstream connector 44′ exposed to pressure due topressurized fluid therein are the slider 152, the valve 151, the centershaft 158 and the upstream threaded adapter 48. Thus by providing arelatively low number of parts exposed to pressure, the chances of aloss of pressure are reduced, and cost and complexity of the assembly42′ can also be reduced.

As noted above, the angled engaging surfaces 180, 190 that transmit theseparation force are similarly internally positioned and protected inboth states of the assembly 42′. Finally, the flow path through theassembly 42′ is relatively straight with relatively little turns andchange-of-direction provided to the fluid, which reduces pressureforces, reduces wear and tear on the assembly 42′, and presents lessopportunities for clogs or flow obstructions.

Pressure-Spike Accommodation—High Pressure

Pressurized fuels may be exposed to pressure spikes due to, for example,connection of the fluid path to a compressor which causes pressurefluctuation during operation of the compressor. Pressure spikes may alsooccur when an operator jerks on the hose 16. Since the fluid iscompressible, but under relatively high pressure, shock waves (which cancome from an upstream source such as a compressor or pump) may propagatethrough the system relatively quickly, presenting a high pressure spikeover a relatively short period of time.

During a pressure spike event of the assembly 42′ of FIGS. 17-20 , sincethe assembly 42′ is pressure balanced as described above, a fluid-basedpressure spike may not directly lead to or cause separation of theassembly 42′. Instead, a fluid-based pressure spike from an upstreamsource may instead apply increased pressure to the seals 164, 166. Theseals 164, 166 may become temporarily comprised and release or “burp”pressure or fluid into the surrounding volumes, such as inner cavity 155of the shaft member 153. It is possible that sufficient burping of fluidor pressure could eventually build up to a degree that relatively strongseparation forces are applied to the assembly 42′. In addition, anexternal separation forces, such as a user pulling on the hose 16 canimpart separation forces that may need to be accommodated. Thus thepressure-spike/separation force accommodation features outlined above,such as the floating magnet unit 43′ and/or floating attraction member106 a, 106 b may be utilized in the assembly 42′ of FIGS. 17-20 .

In particular, as shown in FIGS. 17 and 20 , the center shaft 158 of theupstream connector 44′ may have a retaining ring 132 received in arecess 130 on an outer surface thereof, retaining the washer 134 inplace. When in the coupled arrangement and not accommodating a pressurespike, as shown in FIG. 17 , an axially-extending gap 195 is positionedbetween the washer 134 and the attraction member 106 a, and theattraction member 106 a is biased to the upstream position by spring138.

When the assembly 42′ experiences a pressure spike, the slider 152,magnet unit 43′ and attraction member 106 a, which remains magneticallycoupled to the magnet unit 43′, can move slightly downstream relative tothe rest of the assembly 42, overcoming the spring force of theresilient component 138 and eliminating the gap 195 as the magnet unit43′ and attraction member 106 move downstream. Such relative movementcreates a new gap 197 upstream of the attraction member 106 a, as shownin FIG. 20 , and compresses the spring 138. When in the pressure spikeaccommodating position of FIG. 20 , if a sufficient separation force isapplied to the assembly 42′, the magnet unit 43′ and slider 152 willseparate from the attraction member 106 a and move downstream, and theassembly 42′ will move to the configurations shown in FIGS. 18 and 19 .However assuming that no separation force is experienced, once thepressure spike force is dissipated, the assembly 42′ will return to itsposition shown in FIG. 17 , as biased by the spring or resilientcomponent 138 which seeks to expand back to its original position.

The gaps 195 and/or 197 can be relatively small, such as between about0.005″ and about 0.04″, and about 0.02″ in yet another case since theshocks from a compressor/pump or the like may be relatively short intime. The gaps 195/197 in this case can be relatively small compared tothe gap 137 of the embodiment shown in FIGS. 2, 3 and 13 to ensure thatthere is not movement in the assembly 42′ sufficient to pull any sealsout of position. However, the gaps 195/197 in the embodiment of FIGS. 17and 20 may also be large enough (up to about 0.2 inches in some cases)to accommodate downstream movement of the attraction member 106 a due toa user jerking on the hose 16 in the same manner that a pressure spikemay be accommodated.

Thus, it can be seen that that system described and shown herein canprovide a fluid dispensing system that can use magnetic features toprovide a separation force; that can use magnetic features toaccommodate pressure spikes; that can provide valves that are robust andprovide strong sealing features; that can accommodate pressure spikeswith features other than magnets, and that provide the various otherfeatures and advantages described herein.

Having described the invention in detail and by reference to certainembodiments, it will be apparent that modifications and variationsthereof are possible without departing from the scope of the invention.

What is claimed is:
 1. A breakaway assembly comprising: a firstconnector; a second connector releasably coupleable to said firstconnector, wherein said assembly is movable between a firstconfiguration in which said first and second connectors are releasablycoupled and together define a fluid path through which fluid isflowable, and a second configuration in which said first and secondconnectors are not coupled together, wherein said assembly is configuredto move from said first configuration to said second configuration whena predetermined separation force is applied to said assembly; a closurevalve positioned in one of said first or second connectors, wherein saidclosure valve is configured to be in an open position when said assemblyis in said first configuration to allow fluid to flow therethrough, andto move to a closed position when said assembly moves to said secondconfiguration to generally block the flow of fluid therethrough; anattraction member coupled to one of the first or second connectors; anda magnet unit coupled to the other one of the first or secondconnectors, wherein the magnet unit includes a channel or channels thatincludes a plurality of magnets or a magnet received therein, andwherein a pole of each magnet is oriented perpendicular to a centralaxis of the assembly, wherein the attraction member and the magnet unitare magnetically attracted to each other when the assembly is in thefirst configuration to retain assembly in the first configuration, andwherein the assembly is configured to receive fluid and operate as abreakaway assembly for fluid at a pressure of at least about 2000 psi.2. The assembly of claim 1 wherein said fluid path includes an at leastpartially radially extending portion, wherein one of the first or secondconnectors has a shaft which defines or includes at least part of thefluid path therein and wherein the at least partially radially extendingportion includes or is defined by an opening in the shaft; wherein theclosure valve includes a slider that is configured to sealingly engagethe shaft to seal the fluid path when the assembly is in the closedposition, wherein the assembly is configured to be pressure balancedwhen in the second configuration such that internal pressure-inducedforce is balanced when the assembly is in the second configuration andpressurized fluid is positioned in the fluid path.
 3. The assembly ofclaim 2 wherein the closure valve is configured to move in an axialdirection when moving between the open position and the closed position.4. The assembly of claim 1 wherein the first and second connectors areconfigured to move relative to each other in an axial direction when theassembly moves from the first configuration to the second configuration.5. The assembly of claim 2 wherein the slider is axially slidablymovable along the shaft between the open position and the closedposition of the closure valve.
 6. The assembly of claim 2 wherein theshaft is hollow and has a plurality of radially-extending openings, eachof which is sealed by the closure valve when the closure valve is in theclosed position, and each of which is not sealed by the closure valvewhen the closure valve is in the open position.
 7. The assembly of claim2 wherein the other one of the first or second connectors in which theclosure valve is positioned includes a connection structure that isconfigured to be releasably connected to the closure valve.
 8. Theassembly of claim 7 wherein the closure valve is configured to move inan axial direction when moving between the open position and the closedposition, and wherein the connection structure is configured to axiallymove with the closure valve between the open and closed positions. 9.The assembly of claim 8 wherein the connection structure is configuredto couple the first connector and the second connector when theconnection structure is in a first axial position, and to not couple thefirst connector and the second connector when the connection structureis in a second axial position.
 10. The assembly of claim 7 wherein theconnection structure includes an angled surface on said first connectorand an angled surface on said second connector, and wherein said angledsurfaces are configured to engage each other to retain said assembly insaid first configuration until the separation force is applied to saidassembly.
 11. The assembly of claim 7 wherein the connection structureincludes a plurality of axially-extending, circumferentially-spacedflanges coupled to one of the first or second connectors, wherein eachflange is configured to engage a recess on the other one of the first orsecond connectors to retain said assembly in said first configurationuntil the predetermined separation force is applied to said assembly,and wherein each of the flanges are configured to axially move with theclosure valve when the closure valve moves between the open and closedposition.
 12. The assembly of claim 11 wherein each flange is movablebetween a radially outer position and a radially inner position by aforce applied at a location away a surface of the flange which engagesthe recess, wherein when each flange is in the radially inner positioneach flange is configured to engage the recess sufficiently to retainthe assembly in the first configuration, and wherein when each flange isin the radially outer position the flanges do not engage the recess tosufficiently retain the assembly in the first configuration, and whereineach flange is in the radially inner position when the connectionstructure is in a first axial position, and each flange is in theradially outer position when the connection structure is in a secondaxial position.
 13. The assembly of claim 1 wherein the closure valve iscoupled to at least part of a connection structure which is configuredto releasably couple the first connector to the second connector,wherein the closure valve is configured to axially move from the openposition to the closed position, and wherein the closure valve isconfigured to be magnetically retained in the open position until thepredetermined separation force is applied to the assembly.
 14. Theassembly of claim 13 wherein the closure valve includes or is coupled tothe magnet unit, and wherein the one of the first or second connectorsthat includes the closure valve also includes the attraction member thatis magnetically attracted to the magnet unit to magnetically retain theclosure valve in the open position.
 15. The assembly of claim 13 whereinthe closure valve includes or is coupled to the magnet unit, and whereinthe one of the first or second connectors that includes the closurevalve also includes the attraction member that is magnetically attractedto the magnet unit to magnetically retain the closure valve in theclosed position.
 16. The assembly of claim 1 wherein at least part ofone of the first or second connectors is axially movable relative to aremaining portion of the one of the first or second connectors, or isaxially movable relative to the other one of the first or secondconnectors, when the assembly is in the first configuration and whilethe closure valve remains open, to accommodate force spikes.
 17. Theassembly of claim 16 wherein the at least part of the first or secondconnectors is biased to a rest position by a biasing element, and isconfigured to move axially to an actuated position when accommodating aforce spike.
 18. The assembly of claim 17 wherein the biasing element isfluidly isolated from the fluid path, and is at least one of a resilientmember or a magnet.
 19. The breakaway assembly of claim 1 comprising:wherein any abutting surfaces of the first and second connectors, whenthe assembly is in the first configuration, are at least one of fluidlyisolated or pressure isolated from the fluid path.
 20. The assembly ofclaim 1 wherein at least part of the fluid path is defined by a shaft,and wherein the closure valve is axially movable along said shaftbetween said open and said closed positions.
 21. The assembly of claim 1wherein said fluid path includes a radially extending portion, andwherein when the closure valve is in the closed position the closurevalve blocks the radially extending portion of the fluid path.
 22. Theassembly of claim 1 wherein the magnet unit includes a first portion anda second portion coupled to the first portion that together define achannel therebetween, and wherein the magnet unit further includes aplurality of magnets received in the channel.
 23. The assembly of claim1 wherein the magnetic attraction between the attraction member and themagnet unit defines or primarily contributes to the separation forcethat is required to move the assembly from the first configuration tothe second configuration.
 24. The assembly of claim 1 wherein the magnetunit is annular and extends entirely around the fluid path.
 25. Theassembly of claim 1 wherein at least part of the first or secondconnector is axially movable away from at least part of the other one ofthe first or second connector, while the attraction member and themagnet unit do not move axially relative to each other, to accommodateforce spikes.
 26. The assembly of claim 25 wherein the at least part ofthe first or second connectors is magnetically attracted to the magnetunit, and wherein the magnetic attraction between the at least part ofthe first or second connectors and the magnet unit is configured to beovercome by a force spike when the assembly accommodates force spikes.27. The breakaway assembly of claim 1 comprising: wherein the other oneof the first or second connector in which the closure valve ispositioned is configured to at least temporarily be coupled to theclosure valve when the assembly moves from the first configuration tothe second configuration to positively move the closure valve to theclosed position.
 28. The assembly of claim 27 wherein the closure valveis configured to be positively axially coupled to the other one of thefirst or second connectors when the assembly is in the firstconfiguration and to not be axially coupled to the other one of thefirst or second connectors when the assembly is in the secondconfiguration.
 29. The assembly of claim 2 wherein the slider isconfigured to sealing engage the shaft at a location spaced away from anaxial end of the slider.
 30. The assembly of claim 2 wherein theassembly includes a seal that is configured to sealingly engage theslider on an inner diameter of the slider to seal the fluid path. 31.The assembly of claim 2 wherein the assembly includes an upstream sealpositioned on one axial side of the at least partially radiallyextending portion, and a downstream seal positioned on the other axialside of the at least partially radially extending portion, wherein theupstream seal and downstream seals are configured to sealingly engagethe slider on the radially inner surface of the slider when the assemblyis in the second configuration to seal the fluid path.
 32. The assemblyof claim 2 wherein the assembly includes an upstream seal positioned onone axial side of the at least partially radially extending portion, anda downstream seal positioned on the other axial side of the at leastpartially radially extending portion, wherein the upstream seal isconfigured to sealingly engage the slider on the radially inner surfaceof the slider and the downstream seal is configured to sealingly engagethe other connector to seal the fluid path when the assembly is in thefirst configuration.
 33. The assembly of claim 2 wherein said assemblyis configured to automatically move from said first configuration tosaid second configuration when the predetermined separation force isapplied to said assembly.
 34. The assembly of claim 1 wherein theassembly is configured to be securely retained in the firstconfiguration, and to move from said first configuration to said secondconfiguration when the predetermined separation force is applied to saidassembly, and wherein the assembly is manually reconnectable into thefirst configuration after a separation of the first and secondconnectors due to the predetermined separation force being applied tothe assembly.
 35. The assembly of claim 1 wherein the magnets arepositioned at an angle other than perpendicular relative to a radialline of the breakaway assembly in axial end view.
 36. The assembly ofclaim 1 wherein the plurality of magnets or magnet are configured to bespaced away from and not in direct contact with the attraction memberwhen the assembly is in the first configuration.
 37. The assembly ofclaim 2 wherein the assembly is configured such that any facing orabutting surfaces of the first and second connector, when the assemblyis in the first configuration, are fluidly isolated or pressure isolatedfrom the fluid path.
 38. The assembly of claim 1 wherein the breakawayassembly is biased to a configuration in which the assembly isconfigured to move from said first configuration to said secondconfiguration when a predetermined separation force is applied to saidassembly.
 39. The assembly of claim 1 wherein the breakaway assembly isarranged, in the absence of any outside forces, in a configuration inwhich the assembly is configured to move from said first configurationto said second configuration when a predetermined separation force isapplied to said assembly.
 40. The assembly of claim 1 wherein theclosure valve is configured to not apply any internal forces to causethe assembly to move from said first configuration to said secondconfiguration.
 41. The assembly of claim 1 wherein the closure valveincludes a pair of seals positioned thereon, wherein both seals areconfigured to seal the fluid path when the assembly is in the firstconfiguration, and wherein both seals are configured to seal a portionof the fluid path in the one of the first or second connectors when theassembly is in the second configuration.
 42. The assembly of claim 7wherein the connection structure is configured to be directly releasablyconnected to the closure valve.